Adjustable ratio belt transmission mechanism



T. G. MYERS Filed July 1, 19:59 8 Sheets-Sheet l I N VEN TOR. 7&0/7745 /l/ye/:f

ATTORNEY Aug. 18, 1942.

ADJUSTABLE RATIO BELT TRANSMISSION MECHANISM Aug. 18, 1942.

T. G. MYERS 2,293,617

ADJUSTABLE RATIO BELT TRANSMISSION MECHANISM Filed July 1l 1939 8 Sheets-Sheet 2 v m /6/ l N VE N TOR. Tmaf Mya/1f ATTORNEY Aug. 18, 1942. T. G. MYERS 2,293,617

ADJUSTABLE RATIO BELT TRANSMISSION MECHANISM Filed July l, 1939 8 Sheets-Sheet 3 IN VE N TOR.. 7710/7745 /l//e/j ATTO {ZNEY Aug. 18, 1942- T. G. MYERS ADJUSTABLE RATIO BELT TRANSMISSION MECHANISM Filed July 1, 1959 8 Sheets-Sheet, 4-

INVENTOR /10 n.5 /l//e'ra lav f ATTORNEY Aug 18, 1942- T. G. MYERS ADJUSTABLE RATIO BELT TRANSMISSION MECHANISM Filed July 1, 1939 8 Sheets-Sheet 5 Y f n WM O l T M R \f m5 N m A E 5 T w V A N 0 G 7 n|||||||HU Y ,HHH m HHH mr @m wk. w w m. mmm m. um. www. h. m QM www mw www. KN. ww. SQ.

NS. mx T h- HL! ug. 18, 1942. T, G, MYERS 2,293,617

ADJxJs'lAms RATIO BELT TRANsMlssIoNVMEcHANIsM Filed July 1, 1939 8 Sheets-Sheet 6 I NVENTOR. Tha/w45 WK/:f

ATTORNEY Aug. 18, 1942. T. G. MYI-:Rs

ADJUSTABLE RATIO BELT TRANSMISSION MECHANISM 8 Sheets-Sheet. T

Filed July 1, 1959 hmm.

hkm.

MRM.

INVENTOR. Wwf/M5 /1/ er.;

Pw 5%@ ATTORNEY Aug. 18, 1942. T. G. MYERS 2,293,617

ADJUSTABLE RATIO BELT TRANSMISSION MECHANISM Filed July 1, 1939 8 Sheets-Sheet. 8

INVENTOR TaffmA//erf ATTO RNEY Patented Aug. 18, 1942 ADUSTABLE RATIO BELT TRANSMISSION MECHANISM Thomas G. Myers, Los Angeles, Calif., assigner to U. S. Electrical Motors, Inc., Los Angeles, Calif., a 'corporation of California Application July 1, 1939, 'serial No 282,454

2s claims. (c1. zi-'230.175

This invention relates to a mechanism for transmitting power yby the aid of pulleys and belts; and more particularly to a mechanism in which the ratio o'f the transmission may be adjusted by varying the effective 'diameter of one or more of 'the pulley structures.

Such pulley structures 'usually employ a pair of sections, having opposed inclined faces, adapted -to contact opposite faces of a wedgesha-ped or edge active belt. The sections are made relatively axially adjustable so as to adjust the spacing between the inclined surfaces. The farther apart Tthe'se surfaces are, the closer the belt approaches the axis to Contact these surfaces. Accordingly the effective pulley diameter is decreased by moving the surfaces apart. Conversely, when the sections are vb-roi'ight toward each other, the Ibeltl is urged outwardly from the axis, and the effective pulley diameter is increased.

AIn adapting such pulley structures to various requirements, such as prescribed ranges of ratio transmission, output speed, the power to be transmitted, as well as the space -or location of the mechanism, it has been necessary to manufacture a large variety fof specially designed parts, such as Ycasings, 'and bearings, sizes of belts, etc. A Y

It is one of the objects of this invention to make it possible to utilize standardized partsto fulll the various requirements of a wide variety of installations.

It is another object oi this invention to improve in general the structure and mode of peration of mechanism incorporating such variable diameter pulleys.

In a prior application, filed July 27, 1936, in the name of George T. Pfleger, under Serial No. 92,752, there is Ydescribed a mechanism of this general type. A casing is provided for housing the pulley structure as well as for supporting a source of power, such `as an electric motor'. The mechanism is characterized by the Vcapability of the casing to be swung about the axis of one of 'the pulley structures, in order to make it possible to place the mechanism in the most favorable manner with respect to the space to be occupied by it, and with respect to the position of the loa'd to Ibe driven by it. One aspect vof the present invention is a further extension of these ideas described in said prior application.

By the aid of the present invention, the assembly and removal of the pulleys and ybelts are there are multiple `belts for transmitting large power between the driving and `driven shafts.

Especially when an electric motor is utilized 'as the source of power, the speed reduction and horsepower possible with a single set of belts is at times inadequate; and this is true although the change in ratio obtained by the adjustment in the effective pulley diameters is made as large as practicable. In such instances reduction gearing is resorted to, of the single or multiple type; Aand even a. diierential gear system might be vused to 'bring the speed of the driven shaft substantially to zero. It is 'another object of this invention 'to make it possible readily to utilize any of these types of reduction gears optionally with any of mechanisms.

This invention possesses many other advantages, and has other objects which maybe made more easily apparent from a consideration 'of several 'embodiments of the invention. For this purpose there are shown a few forms 'in lthe drawings accompanying and -forming part of lthe present specification. These forms, which illustrate the general principles of my invention, will now be described in detail; but it is to be understood 'that this detailed description is not to be taken in a limiting sense, since the -scope of my invention is best dened by the appended claims.

Referring to the drawings:

Figure 1 is a View mainly in section of an em'- bodiment of the invention, illustrating a transmission mechanism in which the driven shaft has no 'supplemental reduction gearing;

Fig. 2 is a detail section taken along plane 2;-2 of Fig. 1;

Fig. 3 is a fragmentary sectional view illustrating the addition of double reduction `gearing to the driven shaft of the embodiment of Fig. 1;

Fig. 4 is a View mainly in section of a modification of the invention;

Fig. 5 is a fragmentary sectional view, similar to Fig. 3 illustrating another form of reduction gearing that may be utilized with the apparatus illustrated in Figs. 1 and 4;

Fig. 6 is a view similar to Fig. 1 of a further modication of the invention in which fa reduction gearlof the differential type is utilized for reducing the output speed;

Fig'. 7 is a View partly in section of a still further in'odied form of the invention;

Fig. 8 is a top plan view, partly in section, of a still further modification of the invention;

Fig. 9 is a side elevation of the form of the rendered simple; and this is possible Veven when invention illustrated in Fig. 8;

In the form of the invention illustrated in Figs. 1, 2, 3 and 12, the source of power is indicated as a motor I (Fig. 1) This motor has an extended driving shaft 2. As is common in motors of this type, the end bells 3 and 4 are provided with appropriate bearing structures for rotatably supporting the driving shaft 2. In the present instance the bearing structure in end bell 4 is indicated in section. It may include, for example, a series of balls 5 operating between the inner race 6 mounted on an enlarged portion of the shaft 2, and an outer race 'I mounted in the central hub 8. This central hub 2 is shown as integral with the end bell 4. In order to hold the bearing structure in place a cap 9 may be provided for the boss 8. This cap has a ange which engages the outer race 'I and is held in place as by a plurality of screws I0 passing through a portion of the hub 8. Surrounding the bearing structure is a lubricant chamber I I formed by the aid of the boss 8 and cap 9. Felt lubrication retaining washers I2 and I3 may be accommodated respectively in annular internal grooves in the boss I3 and in the cap 9 for retaining the lubricant in the chamber II.

The end bells 3 and 4 may be provided, as is usual, with Ventilating passageways. Thus for example the end bell 4 is illustrated as having an opening I4 therein for the passage of air into or out of the motor frame 2. This end bell is further shown as provided with the inclined deflector flange I5.

All of this motor bearing structure is merely illustrative as other forms of rotary supports for the driving shaft 2 may be utilized.

In the present instance the motor I is shown as supported on a wall of a frame or casing I6 which serves to enclose and support the important relements of the variable ratio transmission mechanism, such as the variable diameter pulley structures and the belts. For this purpose the left hand wall of frame I6 is shown as provided with an aperture 29. The edge of this aperture is adapted to cooperate with a grooved flange 33 shown as integral with the end bell 4. This flange may be interrupted, and the edge of aperture 29 may be similarly interrupted to provide a bayonet connection between the end bell 4 and the casing or frame I6, somewhat in the manner of a breech lock. As is well known, the elements of such a breech lock mechanism may be separated or united by relative angular rotation of the two elements to establish the connection or to disconnect the members.

In this formv of the invention, a multiple belt arrangement is illustrated involving a pair of driving pulley structures l1 and I8. These driving pulley structures are mounted in driving relation upon the shaft 2 in a manner to be hereinafter described. These pulley structures I'I and I8 are respectively in driving relation to a corresponding pair of driven pulley structures I9 and 20 mounted on a driven shaft 2l.

Each of the variable diameter pulley structures I'I and I8 may comprise a pair of pulley sections 22-23 and 24-25. At least one of the pulley sections such as 22 may be axially fixed to the shaft 2 as by appropriate keys or set screws. Thus through the hub of pulley section 22 there passes a set screw 26 for maintaining pulley section 22 in fixed driving relation to the shaft 2. Pulley section 24 is maintained against axial movement on the shaft by means of a connection to pulley section 22, which will be presently described.

The pairs of pulley sections 22-23 and 24--25 have oppositely inclined faces which engage opposite sides of the edge active belts 21 and 28. By adjusting the relative axial position of pulley section 23 with respect to pulley section 22, the effective diameter of the pulley structure I'I may be adjusted. Similarly by varying the relative axial position of pulley section 25 with respect to fixed pulley section 24, the effective diameter of pulley structure I8 may be adjusted. As pulley section 23 approaches pulley section 22, the belt 2 is forced radially outwardly and the effective diameter is increased. Conversely, as pulley section 23 recedes from pulley section 22, the

belt 2'! is allowed to approach radially toward the axis of the shaft 2, and the effective pulley diameter is reduced.

The adjustments of the axially movable pulley sections 23 and 25 are accompanied by cooperating adjustments of the variable diameter pulley structures I9 and 23 that are mounted upon the driven shaft 2l. Thus if the eective diameter of pulley structures Il and I8 is reduced from the maximum diameter illustrated in Fig. 1, the effective diameters of pulley structures I9 and 23 are correspondingly increased. Further, in order to keep the belts 21 and 23 in alinement between the driving and driven pulley structures, the right hand pulley sections 3I and 32 of pulley structures I3 and 2l) respectively are xed against axial movement on the shaft 2|, while the oppositely facing pulley sections 33 and 34 are axially movable. As illustrated in connection with axially fixed pulley section 32, this pulley section may be held in xed position as by the aid of a set screw 35 passing through the hub of this pulley section. As before, the other xed pulley section -3I is joined to the fixed section 32, so as to be held against axial movement on the shaft.

The mechanism for causing these pulley structures to be adjusted will now be described. In the present instance, the driving pulley structures I1 and IB are arranged to be positively adjusted, and the driven pulley structures I9 and 23 are arranged to be automatically adjusted in response to the adjustment of the pulley structures I'I and I8.

The positive adjustment means for the adjustable pulley sections 23 and 25 includes a thrust bearing structure mounted on the hub 33 of the adjustable pulley section 25. In this way the thrust bearing structure may be moved axially while yet permitting the driving pulley structures and their associated shaft 2 to rotate. In the present instance this thrust bearing structure includes a number of balls 3'I. The inner race 33 of the ball bearing structure is shown as mounted on a reduced portion of the hub 36 and held in place against a shoulder on the hub as by one or more nuts 39 threaded on the end of the hub 35. The outer race 43 of the thrust bearing structure is shown as accom-modated within va cylindrical member 4| and abutting an internal shoulder therein. A cap 42 may be fastened over the left hand edge of the member 4| as by a plurality of screws y'43 passing through the cylindrical member 4| and threaded into the cap 412.

This cylindrical member 4| is arranged to be axially moved but restrained from rotation. As it is moved axially, the thrust bearing structure is correspondingly moved without interfering with the rotation of the rotary parts.

The axial movement of section 25 is transmitted to the corresponding adjustable pulley section 23 of the structure I1. For example, one or more spacer rods 44 may extend between the hubs of pulley sections 23 and 25 and through appropriate apertures in the hub of pulley section 24. The two pulley sections 23 and 25 may be joined together for simultaneous movement as by the aid of a plurality of long screws 45, also extending through appropriate apertures in the hub of the fixed pulley section 24. The `screws 45 serve to clamp the pulley sections 23 and `25 together against the separators 44, thus in effect forming a unitary structure with a vlong hub. It is thus possible by axial movement of the cylindrical member 4| to adjust the axial positions of the pulley sections 23 and 24 simultaneously. The xed pulley sections 22 and 24 are similarly formed into a unitary structure having a long hub, by spacers and screws in their hubs passing through clearance holes in the hub of pulley section 23. A fragment of one of these screws is shown in dotted lines and indicated by 4| A pair of long straight keys, one of which is indicated by 4||l, are oppositely Vdisposed on shaft 2 and extend through both sections 22-23, and 24-25, of ea'ch of pulley structures |1, I8, thereby providing driving relation between shaft 2 and the pulley structures |1 and I.

The manner in which the member 4| is axially moved will now be described. For this purpose the member 4|, which vhas an external cylindrical surface, is guided Yby a sleeve-like extension 46 shown as integral with a cover member 41. This cover member 41 may be supported on the right hand wall of the frame or casing I6 by a breech lock similar to that described in connection with the mounting of motor I. The member 4| is provided with a central threaded boss 48 joined as by the conical wall 49 to the interior of the member 4|. The vconical wall 49 forms with the cap 42, a lubricant retaining chamber D for the thrust bearing structure. The cap 42 may if desired be provided with a felt lubricant retaining washer 5| disposed within a groove in the cap. 42 and engaging the exterior cylindrical surface `of the hub 3S.

Further to maintain lubrication, a llubricant aperture 52 may be provided in the hub of the movable pulley section 123. This maybe closed by an appropriate pressure fitting 53 for the 'accommodation of a lubricant gun.

In order to adjust the member k4| within its guiding sleeve 46, 4use is vmade of a rotary lead screw 54 engaging the threaded -boss 48. This lead screw has an extension 55 for journaling it in the hub 56 of a flange 51 formed integrally with the cover 41. In order to restrain axial movement of the lead screw 54 this extension 55 carries an external collar -58 engaging the right hand surface of the hub '55. The left hand surface of the hub 56 is similarly engaged by a worm wheel 59 secured to the extension 55 and abutting a lshoulder' 5U at the right hand extremity of the extension 55. An oil passage may extend through the lead screw structure for passing lubricant into the chamber 55. This aperture Vmay be closed by a pressure fitting 6|.

The worm Wheel 59 as shown most clearly in Figs. 1 and 2 is arranged to be operated by a multiple thread worm |52. This worm 52 is fixed to a work shaft 63. The worm shaft 63 is rotatably supported at its lower extremity within a boss 64 integral with the flange 51. It is further supported by another hub E5 having an axis normal to the axis of the lead screw 54. It is apparent that by appropriate rotation of the worm shaft 63 the lead screw 54 may be rotated and the axial adjustment of the member 4| thereby accomplished.

In the present instance the rotation of the worm shaft 63 is accomplished through bevel gearing operated manually by a hand wheel 66 fastened to an adjusting shaft |51. This hand Wheel carries at its right hand extremity a driving bevel gear 68 meshing with the driven bevel gear 63 mounted on the top end of the shaft 53. The arrangement is such that the position of the hand wheel shaft 61 may be angularly adjusted for convenience about the axis of the Worm shaft 63. For this purpose the gears 68 and 69 are shown as accommodated in a gear housing 1i] having a detachable cover 1|. The gear housing 1|] has a flange 12 cooperating with the flanges 13 of the hub 55. The two flanges 12 and 13 may be fastened together by any appropriate fastening means which may be released in order to permit relative rotation of flange 12 with respect to flange 13. The worm shaft 53 of course also passes through the flange 12.

The hand wheel shaft 61 passes through the flanges hub 14 formed on the gear housing 1D. In this way the shaft 61 is rotatably supported for rotation of the driving bevel gear 55.

In order to provide a visible indication of the speed adjustment, there is an indicator casing 15 surrounding the shaft 51. This indicator casing has a slot 1G adjacent which a calibrated scale 11 may be supported. Passing through the slot 15 is a pointer 18. This pointer 18 moves axially with respect to the slot 1.6 to cooperate with the scale 11 as shaft 61 is rotated. `For this purpose shaft 51 carries a threaded sleeve 19 attached to the shaft 51 as by a set screw B. The pointer 18 is mounted on a nut 8| threaded on the sleeve 19. Since the pointer 18 is restrained by the slot 15 from rotation, the rotation of threaded sleeve 19 occasioned by operation of hand wheel S6 causes the pointer 18 to be correspondingly moved in an axial direction.

Provisions may be made for limiting the axial adjustment of the member 4| within its guiding sleeve 45. For this purpose a stop bar 82 is provided which is mounted for axial adjustment in an aperture 83 formed in the flange 51 and having an axis parallel to the axis of lead vscrew 54. This stop bar 82 has a reduced extension 84 provided with a head 85 at its left hand extremity. The member 4| is provided with a slot 85 adjacent its lower periphery straddling the extension 84. By this arrangement also, the rotation of the member 4| is prevented. The member 4| has abrupt surfaces at the termination of the slot 85 to cooperate respectively with shoulder 31 formed on the bar 82 and with the head 85 formed at the left hand end of this bar. The

' which the shaft 2i passes.

shoulder 8l and the head 85 thus form limiting stops for the axial movement of the member 4|. These stops may be adjusted by moving the bar 82 in an axial direction after loosening the set screw 88 which engages the bar 82 and holds it in any desired axial position.

Before describing in detail the structure associated with the driven pulley structures I9 and 20 it may be noted that the cover member 4l supporting the adjusting mechanism and the end bell 4 of the motor I may be interchanged in position With respect to the frame I6. In this way it is possible to support the motor I on either the left or right hand wall of the casing I6. Furthermore, the external diameters of the pulley sections 22, 23, 24 and 25 are all somewhat less than the apertures which cooperate with the end bell' and the cover member 4l. In this way it is possible, as described hereinafter, to remove the pulley sections as a unit through one or the other of the casing apertures.

The driven shaft 2| is shown in this instance as supported in appropriate bearings at its right hand end. For this purpose use is made of a cover member 39 having a central hub SII through The central hub t@ serves to accommodate spaced ball bearing structures 9| and 92. The inner race 33 of ball bearing structure 9| is Shown as mounted on the enlarged portion Sd of shaft 2|. edge of the inner race 93 abuts the shoulder Q5 provided on the shaft 2|. The outer race 9G is accommodated within the hub 93. If desired, a felt lubricant retaining washer Sil may be disposed in an annular groove in the hub 93 for preventing the escape of lubricant along the shaft 2 I.

Similarly the inner race 38 of the ball bearing structure 92 is accommodated on the extension 99 of the shaft 2|. It is held in place against the Shoulder IU@ on this shaft as by the aid of one or more nuts It! engaging a threaded portion of the extension 39. The outer race IGZ is accommodated within the hub 93. It is held in place by the cap |313 disposed over the outer edge of the hub Sil. This cap may also be provided with a felt lubricant retaining washer |94, the washers 91 and |24 forming closed lubricant chamber |515, for appropriate lubrication of these bearing structures.

The extension 39 is further extended to form a load driving end |03 of the shaft 2|.

The manner in which the cover member 89 is supported on the wall of the frame I3 will be described hereinafter.

The pulley sections 3| and 32 being fixed to the shaft 2|, and being faced oppositely to the fixed pulley sections 22 and 24 of the driving pulley structures I'I and I3, the belts 2l and 28 will remain in alinement irrespective of the adjustment of the effective pulley diameters. This is true because as the belts 2l and 28 move outwardly along the pulley sections 22 and 24, they also move axially toward the left. As this action takes place the belts 2l and 2S move inwardly with respect to the fixed pulley sections 3| and 32 of the driven shaft 2| and are also moved axially toward the left. The fixed pulley sections 3| and 32 and the movable pulley sections 33 and 34 have hubs which are joined together respectively in a manner similar to that described in connection with the driven pulley structures I'I and I3. These pulley sections 3|, 32, 33 and 34 may be provided with a. pair of long splines as in the case of the driving pulleys The right hand for obtaining proper driving relationship between these sections and the shaft 2|. Similarly, a lubricating aperture III'I may be provided through the hub of movable pulley section 34.

In the present instance, the movable pulley section 33 is constantly urged toward the right by resilient force, such as that exerted by a compression spring I surrounding the left hand extremity of shaft 2|. Since the movable pulley section 33 is joined to the pulley section 34, this resilient force is active to move both of these movable pulley sections in unison, and aS required by the positive adjustment of the driving pulley structures.

In order that there be a radial as well as a thrust bearing support of the left hand end of shaft 2|, thespring |08 is arranged so that its right hand end abuts a shoulder |33 on a sleeve III) mounted on the hub III of the pulley section 33. This sleeve III in turn has its right hand end abutting against the inner ball race |I2 which is mounted upon the hub III. The sleeve III) is held tight against the race ||2 by the aid of one or more nuts |I3 threaded on the threaded left hand end of the hub I I. The outer ball race ||4 is confined within the cylindrical axially movable member I I5, `as by the aid of a cap IIB. This cap IIS has a left hand surface which abuts the right hand edge of the outer race I I4. It may be secured in place with respect to the member II5 as by the aid of a number of screvvs III. Axial movement of the member II5 is effected by the action of the spring |03 and by the reaction of the belts 21 and 28 on the pulley sections 33 and 34. The spring |08 keeps the belts tight under all conditions of operation.

In order to guide the member II5 in an axial direction, it is mounted for sliding movement in the hub II 8 of a cover member II9. The member I5 may carry a spline key |23 adapted to be accommodated in a keyway I2I within the hub IIB.

In order to restrain the left hand end of spring IIS from movement, use is made of a collar |22 threaded on the threaded end of the shaft 2|. This collar may be held in place by the aid of a lock nut |23.

Lubricant may be confined around the ball bearing structure II2, I|4 by the aid of lubricant retaining Washers |24 and |25 respectively accommodated in annular grooves in the member I I5 and in the cap I I'. Lubricant may be passed to the ball bearings' by means of a central aper- 'ture |23 (Fig. 12) which may be closed by a pressure fitting I2'I.

The outwardly projecting end of shaft 2|. past the hub IIS may be protected as by the aid of a supplemental cover member |28 fastened to the left hand edge of the hub I I8.

Due to the interposition of the combination radial and thrust bearing structure between the member I I5 and the pulley section 33, the spring |68 may rotate with the shaft without interfering with the axial movement of the sections 33 and 34.

AS thus far described, it is clear that upon positive axial adjustment of the pulley sections 23 and 25, the spring |68 acts to keep the pulley sections 33 and 34 in proper position in relation to the active edges of the driving belts 2l and 28. When the driving pulley structures I'I and I8 are made to assume la larger effective diameter, the spring ID3 is compressed by the inward movement of the belts 2l and 28 between the respective pulley sections of the driven pulley structures I9 and 20. Conversely, when the Ieffective pulley Vdiameters 'of the pulley lstructures and I8 are reduced, the spring |68 acts to urge pulley sections 33 and 34 toward the right to keep them incontact with the belts 27 and 28.

The cover members 89 and ||9 are supported respectively on the left and right hand walls of the casing or frame I9. These walls have respectively apertures |29 and |39. The outside diameters of the 'sections 3|, 32, 33 and -34 are such that they 'may be passed through either of these apertures |29 and |39. The cover members 89 and ||9 serve to cover these apertures.

However, interposed between the cover member 89 'and the edge of the aperture |29 is an apertured standard |3'| having the spaced feet V|32 and |33. A similar'standard |34 is interposed between the cover member |'|9 of the edge of the aperture |39. The two standards "|3| and |34 are similar 'in construction and are interchangeable. The 'standards 'may `be fastened to the edges of the respective apertures, as by the aid of va number o'f countersunk screws 35, as Well as by bolts |36, the latter being long lenough to pass through the cover members as well as through the standards. Furthermore, the cover members for the standards and the corresponding walls of the frame creasing |6 nest together.

By providing a plurality of angularly 'spaced holes for the screws |35, v|35 it is possible to adjust the angular relationship between the standards |39, |34 `and the frame I6. Thus, vthe bolts and screws |35, |36 are removed, the case rotated about the `axis of shaft 2| to as near the desired position as possible, due regard being had to the necessity of lining up the bolt holes, and the bolts and screws are replaced, serving to secure the case in the adjusted position. ln this way the axis of the driving shaft 2 may be caused to be an'gularly adjusted with respect to the axis of the driven shaft 2|. This is possible by virtue of the 'fact that the inter-nested surfaces of the frame T6, 'the standards 3| and |34 and the cover 'members 89 and H9 are all coaxial with the axis 'of shaft 2 In this manner the adjustment of the mechanism to the required space is facilitated. For example, it is possible by this means to have the 'axes of both shafts 2 and 2| lie in a common horizontal plane or in a common vertica1 plane, or in a common plane that'is oblique to these two planes, depending on the arrangement of the bolt holes.

By virtue of the fact that the 'apertures in the walls of the casing |16 are large enough to pass the pulley structures, the removal and replacement of the pulley structures with respect to the casing of frame l may readily be accomplished. For example, in order to remove the motor with shaft 2 and the associated pulley structures from the casing, through aperture 29, this may be accomplished by loosening the set screw 33 which holds the stop bar 82 in place. Then the bree-ch loci: between the end bell 4 and the casing I6 may be disconnected and the lead screw 54 rotated so as to free it from the member 4|. In this way the member 6| is free to pass out of the hub 46, and the entire structure may be moved axially toward the left.

Similarly, in order to move the shaft 2| with its associated pulley structures I9 and 29, it is necessary merely to remove the cover 89 and to withdraw the shaft 2l with its associated structures, through the aperture |29.

-By the provision -of means, as screws |35, for securing the standards to the frame independently of the cover, the removal of the cover is greatly facilitated; thus by removing bolts |36, the cover, 89 or H9, may be taken off. At the same time the frame is supported as before by standards |3l, |36. It is intended that there be a suihcient number of screws Aand bolts, |36, which are interchangeable to suitably secure the covers and standards in place, as well as to permit the desired angular adjustment Aof the frame `about the axis of shaft 2|, the screws |35 alternating with the bolts |36.

Once the lead screw 54 is disconnected `from the cylindrical member 4|, the belts 21 and 28 may -be dropped far enough down to permit the pulley structures |9 and 23 to be withdrawn in the manner stated. When this is done, then the belts 2 and 28 may be hung upon the retaining bracket |37, so as to render it possible for the pulley structures "I 'I `and |'8 to be moved outwardly through the aperture 29.

The manner in which the device may be reassembled is obvious from the foregoing. Of course in View 1of the interchangeability 'of the end bell 4 and the rcover 4l it is also vnecessary that the cover 89 and the cover 9 may similarly be interchanged. Ein this way the motor may be caused to be supported on either side of the casing I6.

It may scmetimes be necessary to remove the spring |98 for replacement or repair. lThis may vreadily be done by the 'aid Aof `a tool shown in use in Fig. 12, without danger of having the spring |33 expand suddenly and Apossibly cause damage. Y- or this purpose use is made vrof a screw |38 adapted to be engaged in internal threads provided in the 'end of the shaft 2|. On this screw |38 is threaded a nut |32 that has one or more radial handles |139 for manual manipulation. This nut |39 is adapted to abut the collar |22 after the lock nut |23 is removed. By rotation rof nut 4|39 the force of spring A|68 can be 'gradually reduced. Of course, the supplemental cover V|23 must be taken off before this is accomplished.

In case the casing or frame I6 forms an entire enclosure, preferably cover members with ventilating apertures or louvers 'therein may be provided for the front and Abackof thecasing. Such a cover member is shown in Fig. 11. Air can be drawn in through the louvers past the belts and pulley structures, through the end bell `4 and out through the end bell 3 of the motor I.

One of the important features -of the structure described is the ability to substitute a reducing gear mechanism in place Aof the cover member 33, so as to obtain a much more slowly rotating load driving shaft. A double reduction gearing mechanism of this character is illustrated in Fig. 3. In this case the driven `shaft `|'4| which replaces shaft 2| is `shown as provided with a spiral pinion |32, which meshes with a driven gear |43. This gear in turn serves t0 drive the pinion |63 in mesh with a -gear |45. This gear in turn is attached to a load driving shaft |46 which has load 'driving extension |41.

The manner in which shaft 4| and 'the various gears and end Vshafts are supported will now be described. The cover member-89 now carries but one set of ball bearings 9i. The shaft |41, however, has a reduced portion |48 adjacent the pinion |42, and around which another ball bearing structure |49 is provided. The outer race |50 of this ball bearing structure is accommodated in a hub E5| of an 'extension casting |52. The

cap |53 fastened to the left hand edge of the hub serves to retain this outer race |56 in place. The casting |52 may be provided with the air deflecting fiange |56. It may be held in place with respect to the cover member 69 as by the aid of a number of long screws |55 which pass through the casting |52, and threaded into apertures provided adjacent the edges of the aperture |29 in casing |6.

The member |52 is supported by a gear housing |56 which may be conveniently made as a casting. This gear housing is provided with a base |51, having anchor bolt apertures |58, for supporting the housing on an appropriate surface, the housing |56 being arranged to support casing I6 in lieu of the standard |3| of Fig. 1. In order that the parts may be interchangeable, however, a spacer member |59 is inserted between the wall of the casing |6 and the cover 89, having the same cross section as the apertured portion of the standard |35 of Fig. 1. This spacer |59, the frame I6 and the cover member 89 inter-nest in the same manner as the corresponding parts in Fig. 1.

The housing |56 is provided with an intermediate wall |66. Adjacent the lower part of the wall as seen in Fig. 3, there is an aperture |6| in which is disposed a ball bearing cage |62. This ball bearing cage |62 supports the outer race |63 of a ball bearing structure |66. This ball bearing structure rotatably supports a shaft |65 upon which the driven gear |43 is supported. The gear |43 as heretofore stated is in mesh with the driving pinion |62,

The shaft |65 also carries the wide driving pinion |44 which is in mesh with the gear wheel |45. The right hand end |66 of shaft |55 is rotatably supported by the aid of a ball bearing structure |61. The outer race of this ball bearing structure is supported in a flange or boss |68 formed integrally with the gear housing |56.

The shaft |46 upon which the driven gear |45 is mounted is supported at its left hand end by the aid of a ball bearing structure |69. The outer race |16 of this ball bearing structure is supported in a hollow boss |1| located above the aperture |6| in the wall |66 as seen in Fig. 3. The right hand end of the shaft |46 is shown as supported by the aid of a ball bearing structure |12. The outer race |13 of this ball bearing structure is supported in a supplemental cover member |14 fastened to a flange |15 formed on the gear housing member |56. This cover member |14 may be provided with a boss |16 in which one or more felt lubricant retaining washers |11 may be disposed.

An oiling disk |18 is shown as fastened to the shaft |46 to distribute the oil in the gear housing members to the various bearing structures. Lubricant may be placed within the housing |56 for this purpose, into which the disk |18 projects.

Whether the mechanism incorporates the reduction gearing of Fig. S or not, it is yet possible to adjust the relative angular position of the axis of the driving shaft 2 with relation to the axis of the driven shaft 2| or |4|. This is accomplished when the reduction gearing of Fig. 3 is utilized by simply removing and replacing the bolts |55, as described in connection with bolts |35, |36 of Fig. 1.

The intermediate housing |52 is arranged to be fastened to the housing |56 by the aid of the screws |19 which pass through a iiange |86 of the member |52 and which are appropriately threaded into threaded apertures in the flange |8| of the housing |56.

In order to supply the lubricant to the gearing housing |56 a filler plug |82 may be provided, leading to a passageway that is in communication with the interior of the housing |56.

In the form just described, a multiple belt drive is disclosed. However, this is not essential in the event that a smaller amount of power need to be transmitted. Thus in the form of Fig. 4, a single belt drive of the same general character as heretofore described is shown. In this instance the casing or frame |83 is shown as being provided with an aperture |84 in its left hand Wall for the accommodation of an end bell |85 of an electric motor |86. This end bell |85 may `have a breech lock connection with the edge of the aperture |84 as heretofore described. The motor shaft |81 may be rotatably supported by the aid of a ball bearing structure |88 supported in the end bell |85 in a manner quite similar to that disclosed in Fig. 1.

The shaft |81 in this instance carries an axially xed pulley section |89. This pulley section cooperates with an axially yadjustable pulley section |96 forming the variable diameter pulley |9|. The hub |92 of the pulley section |89 may be fixed to the shaft |31 as by the aid of a set screw |93. Both pulley sections |89 and |96 may be appropriately splined to the shaft |61, as by one or more keys 4|2. This adjustable pulley section |96 may be moved in an axial direction by mechanism quite similar to that disclosed in Fig, 1. For example, the hub |94 of the pulley section |96 supports the inner race of a thrust ball bearing structure |95. The outer race is supported in a cylindrical member |96 of the same general construction as cylindrical member 4| of Fig. l. This member |96 is shown as guided for axial movement in a hub |91 of a cover member |98 for the frame aperture |99. As before, the member |96 is adapted to be axially adjusted by the aid of a lead screw such as 266. This lead screw has a cylindrical extension 26|.

In this instance a slightly dierent form of mechanism for rotating the lead screw 266 is illustrated. Thus instead of a worm and wheel construction, a bevel gear construction is illustrated. A bevel gear 262 is mounted upon the right hand extremity of the extension 20|. Its hub is journaled in the end ange 266 of the cover member |98. A collar 264 fastened to the extension 26| outside of the flange 263 may be fastened to the extension 26| to prevent axial movement of the lead screw 266.

In order to rotate the bevel gear 262, there is provided a driving bevel gear 265 mounted on a shaft 266. The axis of this shaft is perpendicular to the axis of lead screw 286. It is journaled in a boss 261 formed on the cover member |98. The shaft 266 projects upward through a boss 266 formed integrally with the gear housing 269. At the top end of the shaft 268 there is disposed a driven bevel gear 2|6. This bevel gear meshes with a driving bevel gear 2|| fastened to a hand wheel shaft 2|2. This hand wheel shaft 2|2 may further be supported by a standard 2|3 fastened to the top of the casing |83. An indicator mechanism 2|4 may be arranged in a manner similar to that disclosed in Fig. 1.

It is noted that in this case also, the aperture |64 and |99 are large enough to permit the passage of the entire pulley structure through these apertures. This can be accomplished as before by releasing the set screw 2 I5, which holds the stop bar 2|S in adjusted position, and by releasing the breech lock between end bell |35 and the aperture |84. Thereupon upon rotation of lead screw 260 the cylindrical member |96 may be freed from the lead screw to permit the motor shaft |81 with its associated pulley structure to be withdrawn from the casing through aperture |84.

The driven shaft 2|1 in this instance is supported solely by a pair of spaced ball bearing structures 2|3 and 2|9. The outer races of these ball bearing structures are accommodated within a hollow boss 22B formed integrally with the cover member 22|. This cover member is of the same general construction as cover member 89 of the form shown in Fig. l. As before, there is interposed a standard 222 between the cover member 22| and the edge of the frame aperture 223. A similar standard 224 is interposed between a cover member 225 at the left hand end of the frame |83 and the edge of the left hand aperture 22B.

The driven pulley structure 221 in this instance includes an axially fixed pulley section 228. This pulley section 225 has an elongated hub 229 which is xed to the left hand extremity of the shaft 2|1. Splined to the hub 229 is the hub 235 of the movable pulley section 23|. This movable pulley section is constantly urged toward the right by the aid of a compression spring 232 disposed around the hub 23B. The left hand end of this compression spring is restrained against axial movement by the aid of a collar 233 threaded into the elongated hub 229. A lubricating aperture 23d may be provided through the collar 233.

The driving pulley structure i9| and the driven pulley structure 22! cooperate with an edge active belt 235 which transmits the power from one pulley to the other.

The apertures 223 and 225 in the frame |33 are large enough to permit the pulley structure 221' to pass through them. In order to remove the pulley structures, the same general procedure is followed as in connection with the form shown in Fig. l. A belt retainer strip 235 may be used upon which to hang the belt 235 while the pulley structures are withdrawn from the casing |83.

In this form also it is possible to adjust the angle of the axis of driving shaft |81 with respect to the anis of driven shaft 2l1. This is accomplished by removing the bolts 231, 238 which serve to fasten the cover members and the standards to the frame |83.

While as disclosed in Fig. 3, a double reduction gearing may be utilized, it is possible to substitute therefor a single reduction gearing. Such a form is illustrated in 1Eig. 5. In this case the cover member 22| for the aperture 223 is shown as having a gear housing casting 253 supported thereon by the aid of a plurality of bolts 24| which pass through the housing 245 as well as through the cover member 22 I, the standard 222 or |3i, and into treaded lapertures adjacent the edge of the aperture 223.

The gear housing 24E) has an intermediate wall 242 by the aid of which the various bearing supports may be supported. This wall 242 also provided an air inlet passage 243 for the interior of the casing- The driven shaft 244 in this form of the invention carries at its end a driving pinion 245 which meshes with a driven wheel 243. This driven wheel isV mounted upon the load driving shaft 241.

The right hand end of shaft 244 in this case is shown as supported by the aid of a ball bearing structure 243. The outer race of this ball bearing structure is accommodated within the hollow boss 2413 integral with the wall 242. This outer race is retained in place by cap 253.

The left hand end of the load driving shaft 241 is supported by the ball bearing structure 25| suitably supported in wall 242. The other end of shaft 2631 is supported by a ball bearing structure 252. The outer race of this ball bearing structure is accommodated in a cover 253 fastened to the left hand edge of the housing 245.

The chamber 254 formed between the wall 242 and thercover 253 may be utilized as a lubricant chamber. In order to prevent excessive loss of lubricant, felt lubricant retaining washers 255 may be provided in the cap 253. An oiling disk 251' may be fastened to the right hand extremity 'of the shaft 24.4 and arranged to have its edge disposed within the lubricant. The shaft 241 may have a tapered portion 253 which serves to guide any lubricant caught on this shaft back into the chamber 25d, instead of allowing it to creep outwardly along the shaft 241.

The single reduction gear illustrated in Fig. 5 is interchangeable with the double reduction gear illustrated in Fig. 3. Either of them may be used as required by the conditions of the load. Either the single or double reduction gearing' with the housing therefor, may be utilized to cooperate directly with a motor shaft; in this case the gear housing replaces a motor end bell.

It is not necessary that the mechanism incorporate any specic form of reduction gearing. In fact, in some instances a differential reduction gear may be used effectively, especially where it is desired to reduce the speed of the output shaft to comparatively low values. Such a system is described and claimed in a prior applicationr pending in the name of Den Heyer and George T. Plieger, Serial No, 679,335, filed July ll, 1933, entitled Variable speed power unit. This type of reduction gear is shown embodied in the form of the invention illustrated in Figs. 6 and 14.

In Fig. 6 the casing or frame 253 is shownas having the same general structure as the casing or frame I6 of the form shown in Fig. l. In this instance also, the electric motor 263 is shown as mounted by the aid of a breech lock connection between its end bell 26| and the edge of the aperture 2'52. The driving shaft 253 is supported in general in a manner substantially identical with that illustrated in Fig. l. In` this instance, however, in addition to the two driving pulley structures 264 and 265, the shaft 263 carries a fixed diameter multiple belt pulley structure 233. This multiple belt xed diameter pulley structure is utilized to drive one of the elements of the differential gearing later to be described. The variation in effective diameter of the two driving pulley structures 264 and 265 is4 accomplished by the aid of a lead screw mechanism in association with a sliding cylindrical member and a guide, this adjusting structure in general being designated by the reference character 261. The hand wheel 268 for operating the adjusting means is shown as mounted in a vertical position, as for example as by being directly connected to a shaft that operates the lead screw. As before, this adjusting mechanism is supported by the aid of a breech lock connection in the aperture 239 in the frame 259. The motor 260 with shaft 253 and the associated mechanism may be withdrawn through the aperture 262. As before, the position of the motor 299 and the adjusting mechanism 281 may be interchanged with respect to the frame 259.

The multiple driving belts 219 and 21| are shown as in driving relation to a pair of driven pulley structures 212 and 213. These pulley structures are shown as in driving relation with a hollow shaft 214, forming one element in a differential gear drive. This hollow shaft 214 is rotatably supported adjacent its right hand end by the aid of a ball bearing structure 215. The outervrace for this ball bearing structure is shown as accommodated in a boss 219 shown as formed integral with a gear housing 211. This gear housing 211 may be provided with a flange 218 overlapping the edges of the aperture 219 in the right hand side of the casing 2'59. By the aid of the flange 218 the housing 211 may be attached to the frame 259.

The axially adjustable pulley sections 299 and 28| of the driven pulley structures 212 and 213 are urged in unison toward the right by the aid of a compression spring 282 embracing the hub of the section 289. The operation of the pulley structure is substantially the same as that disclosed in connection with the driven pulley structures 9 and 29 of Fig. 1. The left hand end of the spring 282 is restrained against outward movement by the aid of a collar 283, having the sleeve extension 284. This collar is held against a shoulder on the shaft 214, as by the aid of a nut 285 threaded on the threaded extremity of the shaft 214,

The sleeve 284 serves to support a ball bearing inner race 298. The ball bearing 281 is utilized to support the shaft 214 rotatably at its left hand end. The manner in which the outer race 288 of this ball bearing structure is supported will be described hereinafter.

The speed of the shaft 214 is controlled by appropriate manipulation of the hand wheel 293. The motion of shaft 214 is transmitted to one of the elements of a differential gear mechanism. In this instance this differential gear mechanism is shown as including planetary gears, the details of which will be hereinafter described.

Another of the elements of the differential gearing is adapted to be driven by the aid of the shaft 289, which is coaxial with and disposed within the hollow shaft 214. This shaft is rotatably supported at its left hand extremity by the aid of a cover member 299 having a flange which overlaps the aperture 29| in the left hand wall of the casing 259. As before, interposed between the cover member 299 and the edge of aperture 29|, there is a standard 292 having supporting feet 293.

Telescoping with the left end of the shaft 289 is the hub 294 of a xed diameter pulley structure 295. This hub is appropriately fastened to the shaft 289, to be in driving relation therewith, and is held in place as by the aid of one or more nuts 299 threaded on the end of the shaft 289. The hub 294 serves to accommodate the inner races 291 and 298 of spaced ball bearing structures for supporting the left hand end of the shaft 289. In order to space the races 291 and 298 in this manner, use may be made of a spacer sleeve 299.

The outer races 399 and 39| of these bearing structures are accommodated within the hub 392 of the cover 299. A supplemental cover 393 may be provided for the end of the hub 392. This supplemental cover 393 in conjunction with the felt lubricant retaining washer 994 adjacent the right hand end of the hub 392 forms a chamber in which lubricant may be confined for the bearing structures.

In the present instance the pulley 295 cooperates with the driving pulley 259 on the motor shaft 253. These pulleys may be provided with a plurality of V-belts 395. The pulley structure 295 serves to support the outer race 288 for the ball bearing structure that rotatably supports the hollow shaft 214. This is accomplished by providing an appropriately formed recess within the body of the pulley 295. The outer race is held in place by the aid of a anged ring 396 fastened to a flange 391 formed integral with the body of the pulley structure 295. This flanged ring 399 may carry a lubricant retaining felt washer 398 cooperating with the outer surface of the collar 283. In this way, lubricant may be retained in the space within the body of the pulley 295 in which the ball bearing structure is accommodated.

Provisions are made in connection with pulley structures 295 to maintain the V-belts 395 in proper operative engagement with the grooves of the pulley. For this purpose, a ring 399 of wedge shaped cross section is slidably mounted on the cylindrical cup-like flange 3|9 of the pulley 295. The opposite surfaces of this ring 399 cooperate respectively with the adjacent sloping surfaces of the belts 395. The pulley structure 295 is also `provided with a flange 3H at its left hand end for cooperating vwith the left hand side of the left hand belt 395. The right hand side of the right hand belt 395 is arranged to be in operative Contact with the sloping face of another ring 312, which is also slidable on the cylindrical portion 399. This ring 3| 2 is urged resiliently toward the left, as by the aid of a plurality of compression springs 3|3. These compression springs are arranged around the periphery of the cylindrical member 399; and their right hand ends abut the flange of a ring 3M fastened to the end of the cylindrical portion 395. In this way a thrust is transmitted not only to the right hand belt 395 but through the belt to the sliding ring 399, for keeping both belts in proper frictional contact with the driven pulley structure. Guides may be provided for the plurality of compression springs 3|3, as by the aid of the studs SI5 fastened to the ring 3M.

As thus far described, it is apparent that the shaft 289 has imparted to it a constant speed of rotation, while the hollow shaft 214 has an adjustable speed. In the present instance, the constant speed shaft 289 is shown as having a speed comparable with the lowest speed obtainable for the shaft 214.

These two shafts 214 and 289 are utilized to operate the elements of the differential gear mechanism. Thus the hollow shaft 214 has keyed to it at its right hand end, a spur gear 3|5 which has an overhanging hub portion 3|1. Within this hub portion is accommodated the outer race of a ball bearing structure 3|8, for supporting the right hand end of the constant speed shaft 289. Also, this right hand end of the constant speed shaft 289 carries a spur gear 3 9.

The gear 3|6 and the gear 3|9 are in mesh respectively with pinions 329 and 32| rigidly mounted upon the shaft`322, that is intended to revolve in planetary fashion about the common axis of shafts 214 and 289. It is apparent that by appropriate choice of pitch diameters for the gear members 3|5, 3|8, 329 and 32|, there will be imparted a planetary motion to shaft 322 which depends upon the relative .speeds of shafts 214 and 2.89..

-There may bea plurality of such shafts as 322 With sets Aof gears .3211 and `32| mounted thereon. `Under lany circumstances .the ends f the shaft 322 are mounted insucha way as to permit this planetarymotion, .and also t0 impart this planetary .motion to a load driyingshaft. Thus the left hand end of .the shaft 322 is rotatably supported by a ball bearing structure 323. The outer race .0f this "ball hear-ing structure is accommodated .in ,a @unlike housing 4.monitor 324. This housing member has Ia hub portion 325 mounted for free rotation on the shaft `214 as by the aid 0f the ball bearing structuren@ The righ-t hand end o f the shaft 322 is shownlas supported by the Aaid of the b all bearing structure 321. The outer race of this structure is accommodated within an appropriate aperture in ,a Covering disk 328 for the lcup-like member 324. This disk is vaccommodated on the lef-t `hand tend Y329 of a load driving sha-ft 3351. The d isk 32,8 may b e attached to the shaft 3.3.0as-by the aid of a plurality of screws 33|, which engage a flange `332 integral with the shaft 330.

This shaft 333 in turn `may be rotatably supported by the'aid of the standard 333 fastened to the right hand end of the gear housing 211. This standard 33.3 is similar in structure to the standard 232 at the left hand .end ofthe apparatus. These `two standards may serve to support the `fra-4me in any of a plurality of angular positions about :the axisof the shafts 234 and 289. The shaft 33|) yis rotatably supported in the standard 33,3 `by the aid of the `ball bearing structure 334. -T-lie inner race of this ball bearing structure is fastened to the shaft by the aid of the threaded nut 335. The `outer race is accommodated in the boss 33t.

In order that the differential gear mechanism may be provided with lubricant, the Vgear housing 211 may serve to accommodate any appropriate lubricating medium. A felt washer 331 in the boss 21S serves to prevent passage `of .the lubricant out of the housing 211 toward the left. Simi- Y Y larly, a felt washer 33.8 may be accommodated in an annular groove in the boss 335 to prevent loss of lubricant at the other end of the gear housing.

The mode .of operation .is apparent from the foregoing. By appropriate manipulation Aof the hand wheel 25.8, the rate of rotation of the load driving shaft 33|] may be adjusted Within very w-ide limits. The assembly vand replacement of the pulley structures and their associated parts are accomplished in a manner similar to that described in connection with Fig. -1. In order to remove the driven shafts 2.24 and 28S it may be necessary first to .remove the nuts 296 to permit withdrawal of the pulley 295 without disturbing the ball bearing structures 291and 2.93. Of course, -the apertures 262, 2559, `215| and 29| are made large enough to permit passage of the pulley structures .out of thecasing.

It may be advisable at times to supplement the differential gear reduction with ,a further train of reduction gears. This is readily accomplished by supporting the reduction gear by the aid of the :gear housing 211. This structure is illustrated in Fig. 14,

In this structure, the shaft 330 is shown as carrying a driving pinion 339 gwhichmeshes 4.w-itlfi a driven gear 343. This jdrivengear is mounted upon a `'load driving shaft 34|. rIhis reduction -gear is entirely similar to the reduction gearing illustrated in 5, the gear 'housing casting 240 and its cover 253 being identical with the similarly numbered parts of Fig. 5. However, the standard 34.2 differs from the standard 333 of Fig. 6 by the addition of a ange 343 for proper interiitting with the left hand edge of the casting 240. This standard 342 of course is provided with appropriate supporting feet 344, and may be utilized to support the entire structure in any one of a number of annular positions about the axis of the driven shafts.

In the form of the invention illustrated in Fig. 1, the motor I is shown as directly `mounted upon the frame I6 by the aid of the end bell 4. Itis possible, however, to provide merely a coupling for the mechanism, and a bracket support for the motor l which may later be coupled to the driving shaft. Such an arrangement is shown in Fig. 7. In 4this form of the invention the driving shaft 3 45 serves the same function `as the driving shaft 2 in Fig. ,1. It carries substantially identical driving pulley structures 3.43 and 331 as in that figure. Furthermore, the effective diameters of these pulley structures may -be varied by the aid of the hand wheel 66 as in the rst form.

The aperture 348 `at the left hand side `of the frame I6 in this instance is arranged to form a breech lock connection with a supporting .cover structure 349. This supporting cover structure has a hub portion 35B. Within this hub portion is accommodated the outer race 35| of the ball bearing structure 352 that supports the left hand end of the shaft 345. This ball bearing .structure is held in place against a shoulder 353 on the shaft 3.45 as by the aid of nuts 354. A cap 355 ymay be provided for the hub 35,0 `and vheld in place as by the aid of a plurality of screws 35,6. -The shaft 365 extends outwardly through the `cover structure 349 and carries at its outer end a coupling flange 351.

The ball bearing structure 352 may be provided -with lubricant, there being a space conlined by the hub 3.50 and cap 355 for this purpose. Lubricant felt retaining washers 358 and .359 'may -be provided in the manner heretofore described for confining the lubricant within vthe bearing enclosure.

The driving electric motor 33,3 is shown in this instance as having a coupling flange 36| adapted to be `fastened to the coupling flange V351. The motor as a whole is mounted upon a bracket .41.3. Tghis bracket has vertical 4wall 362 fastened -to rthe outside of the cover member 349, as by the aid 4of a plurality of screws 333.

In the `adjustment of the apparatus illustrated in Fig. '7, the axes of the driving and .driven shafts are in a common vertical plane, which is one of the positions of adjustment ofthe frame |;6 .about the axis .of lthe driven shaft. As this plane maybe adjusted to an oblique plane or to a horizontal plane Aas illustrated in Fig. 1, the bracket 4i|3 may be -correspondingly adjusted to maintain its position for supporting the motor 33E) on a horizontal support.

Instead of the coupling arrangement illustrated in Fig. 7, the source of power may rb-e connected in .other ways to the driving shaft. In the form illustrated in Figs. 8 `and v9, for example, .the `frame 334 is shown for enclosing most of the operating lparts of the structure. Here the driving shaft 365 is shown `as rotatably supported by an end bell structure 18,5, substantially identical with the end bell structure shown in Fig. l. In order to provide another bearing support vfor the shaft 365, it is extended toward the left for accommodating another bearing structure 383. This bearing structure is accommodated in an end bell 381 of the same general structure as the end bell 3 of Fig. l. The

end bell structures 361 and |85 may be fastened to an intermediate supporting standard 338 having the supporting feet 389.

The bearing structure 358 may be urged against the shoulder 318 of the driving shaft 355 by the aid of the nut 31|. The outer race 312 is accommodated within the boss 313 of the end bell 351, and is held in place by the cap 314. This cap 314 is fastened as by bolts 315 to the boss 313. As before, lubricant retaining washers 318 and 311 may be provided for retaining lubricant within the chamber formed by the boss 313 and the cap 314.

As in the other forms, the assembly and replacement of the pulley structures may be accomplished in a simple manner. Furthermore, the axes of the driving and driven shafts may be adjusted to lie in a vertical or horizontal plane or an oblique plane, by appropriate manipulation of the bearing standard members |3| and |34. The end bell 381 may also be angularly adjusted with respect to the axis of the driving shaft 385.

Instead of coupling the driving shaft directly to a source of power, this coupling may be effected by other means, such for example as a belt transmission. Such a form is illustrated in Figs. l0 and 11.

In this form of the invention, the frame 18 may be identical with that described in connection with Fig. l. The driving and driven pulley structures may likewise be similar, as well as the adjusting mechanism including the hand wheel 66. Instead of mounting the source of power directly on the left hand wall of the casing I5, the end bell 318 is mounted there, by the aid of a breech lock in the frame 18. This end bell together with the end bell 319 are generally of the same construction as illustrated in Fig. 8. In this form, however, the bell 318 may be also provided with feet 388. This, together with the feet 38| on the supporting standard 392 intermediate the two end bells 318 and 319, may be utilized for supporting a source of power, such as the electric motor 383. Thus with the end bell 318 and the supporting standard 382 adjusted angularly to bring these feet 389 and 38| in a common angular position, these feet may be used to provide a rest for a at bracket 384. On this bracket may be supported the electric motor 383. The bracket 384, the standard 382, the end bell 318 and the motor 383 may be appropriately fastened together, as by bolts passing through the feet 38|, and through the bracket 384.

The motor 383 is shown as coupled by a pair of belts 385 to a multiple pulley structure 388 mounted on the end 381 of the driving shaft. The motor 383 carries -a corresponding multiple belt pulley 388 around which the belt '385 extends.

As before, the angular position 0f the axis of the driving shaft with relation tothe axis of the driven shaft may be adjusted by appropriate manipulation of the main standards |31 and |34. Likewise the end bells 318 and 319 with the standard 382 may be independently angularly adjusted about the axis of the driving shaft.

Although in Fig. l there is illustrated a variable power transmission structure utilizing a pair of belts for transmitting power between the driving and driven shafts, the number of belts and pulleys may be varied. For example, in Fig. 13 the frame 389 is shown wide enough to accommodate a structure utilizing three belts in multiple. These belts are indicated by reference characters 398, 39| and 392. There are three driving pulley structures 393, 394 and 395 upon the driving shaft 398. The electric motor is shown as of identical construction as in Fig. l.

In order that all three of the adjustable pulley sections of the driving pulley structures be moved simultaneously, the coupling rods 391 may be extended through the intervening fixed pulley sections. This arrangement is illustrated in connection with the driven pulley structures 398, 399 and 489. In all other respects the structure is similar to that illustrated in Fig. 1. They are connected by a number of through bolts and spacers in the same manner as the pulley sections of the double belt arrangement of Fig. l. The fixed sections are connected as illustrated in connection with the driven pulley structures 398, 399 and 489. Thus a plurality of bolts, one of which is indicated by 414, extend from the fixed section 411 of pulley structure 498 to the fixed section 418 of pulley structure 398, passing through clearance holes in the intervening fixed section 419 of pulley structure 399, as well as in the movable sections of pulley structures 399 and 499. Spacers, as 415, are interposed between fixed sections 411 and 419, and similar spacers 4|6 are interposed between fixed sections 419 and 418. Thus, the three fixed pulley sections are in effect formed into a unitary structure with a l-ong hub. The adjustable sections are formed into a unit in a similar manner, fragments of the bolts and separators being dotted lines at 439 and 42|.

What is claimed is:

1. In an adjustable ratio transmission mechanism, a driving shaft, a driven shaft, a plurality of adjustable diameter pulley structures on each shaft, each of said pulley structures having a pair of relatively axially adjustable pulley sections with opposed inclined belt engaging faces, forming by relative axial adjustment, variable effective pulley diameters, means for adjusting the relative axial positions of the pulley sections on each shaft, as well as providing a bearing support for said shaft, means connecting the hubs of alternate movable pulley sections so that said sections are slidable as a unit along the associated shaft, a frame for the mechanism, and means providing a second bearing support for each of the shafts and detachably supported by the aid of the edges of apertures in the frame, said apertures being large enough to permit withdrawal of the respective shafts and their pulley structures through the apertures, said adjusting means including an axially slidable thrust bearing structure associated with that section which is farthest from the bearing support for the shaft, a 'guide means supported on the frame for said thrust bearing structure, and means, detachable from the thrust bearing structure, for axially adjusting said thrust bearing structure.

2. In an adjustable ratio transmission mechanism, a driving shaft, a driven shaft, a plurality of adjustable diameter pulley structures on each shaft, each of said pulley structures having a pair of relatively axially adjustable pulley sections with opposed inclined belt engaging faces, forming by relative axial adjustment, variable efindicated by ,fectivepulleyfdiametera means for-adjusting the .relative axialpositions of =the pulley Asections von each shaft, `as -.Wel1 Lasr'providing a lbearing-support Cforsaid-shaft, :means connecting thehubsiof alternate movable 'pulley 'sections `so that 'said `sections .are slidable fas a unit along the associated shaft, a frame for Vthe mechanism, tand .means providing a `second bearing support for each of the shafts and-detachably supported 'by the aid of the edges .of apertures ein the fra-me, said apertures being large enough ltoipermit withdrawal of the respective ,-*shaftsand their pulley `structures through the apertures, said means .that provide bearing supports ,-for Tone lof ythe shafts ,including standards -serving also-as a.y sup- -port fortherframe, by-theaid of which-standards the vframe may be langularly adjustedabout `the :axisof said one of theshafts.

ing by relative axial adjustment, xvariable effec- 4 :tive pulley diameters, :means connecting the -hubs -of alternate movable pulley sections .-so lthat-said sections are slidable asa unit along the associated shaft, aiframe for the mechanism, -means providinga-bearing support .forfone endof one of theshafts and -detachably-supported bythe aid of the edge of an aperturein-the frame, said Yaperture-being Vlarge enough sto permit withdrawal of the .said one-of=theshafts and its associated pulley structures Ythrough the aperture, a spring associated with that pulley section -on `Athe said one of the shafts which is farthest from the .bearing support, a slidable thrust bearing struc- -ture associated .with said section, and a ,guide means supported on Ithe frame, rfor said thrust bearing structure.

4. `Inan adjustable ratio transmissionmechanism, a vdriving shaft, a driven shaft, an Yadjustablediameter pulley :structure onrone of the shafts, lhaving a A,pairof -relatively axiallyadjust- .ablepulley sections with.opposed.inolinedbeltfengaging faces, forming 4by relative axial adjustment, variable effective pulley diameters, a frame for .the mechanism, means providing a bearing ,support foroneendfoffone-of theshafts and "detachablysupported bythe aidofpthe edge'ofan aperture Vin the jframe, said-aperture -being large enoughto-permit withdrawal Iof thessaid one rof the shafts and its associated pulley structure through the aperture, -a springassociatedwith that .pulley section which is .farthest -frorn the bearing support, a slidablethrust-bearing'structure .associated -with said section, and a 4.guide means supported on the frame, for said ithrust bearing structure.

l5. In an adjustable .pulley structure, ,a shaft, a pair of relatively axially adjustable pulley sections with opposed inclined belt engaging faces, forming ,by relative axial adjustment, variable effective Vpulley diameters, --a )collar vthreaded fon the ,end of lthe shaft, .a spring yabutting the :collar and `associatedwith the adjacent vsection "to urge vsaid section axially along the shaft, said shaft having Ya threaded aperture at 'its end, ra threaded element for-engaging `said aperture, and a nut member engaging -the threaded Aelement servingfas an abutment 'for the collar-,upon unscrewing the collar from the shaft.

v 6. Inan adjustable -ratio transmission :mechanism, a .driving shaft, a ,driven shaft, one or more adjustable diameter pulley structures 'on .the driving shaft, onefor more pulley'struotures ported by the bearing means for thesupplemen- 'tal shaft, means transmitting A,power from the driven shaft to the supplemental shaft, a second bearing means for the other end "of the hollow shaft and detachably Supported by the frame, and a differential Ygear -mechanism associated with both the hollow shaft-and-the-1supplemental shaft adjacent ltheend where the said second bearing means for the hollowshaft is located.

'7. In an adjustable ratio transmission mechanism, a driving shaft, a driven shaft, 'one or more adjustable diameter pulley structures .on the drivingshaft, one or more pulley structures on said driven shaft, a frame -for `supporting.said shafts, belt means engaging the pulley structures for driving said driven shaft, said `driven shaft being hollow, a supplemental shaft extending throughthe hollow shaft, bearing means for one endfof the supplemental shaft, supported by the frame bearing means `for said hollow ,shaft supported by the bearing means for Athe supplemental shaft, means transmitting power `from the driven Vshaft "to the supplemental shaft, a second bearing for the other-end of the hollow shaft and ldetachably supported by the frame, a differential gear mechanism associated with both the hollow shaft and the supplemental shaft -adjacent the endwhere the said second bearing means for the hollow shaft-is located, said second bearing means having a housing extension for ,the differential gear mechanism, a cover member `for the extension, and a load driving shaftextending through the cover member.

8. ,In an adjustable ratio'transmission mechanism, a driving shaft, an adjustable diameter pulley structure on the-shaft, said structure having a pair of relatively-axially adjustable pulley sections with opposed inclined belt lengaging faces, forming by relative axial adjustment, variable effective pulley diameters, a driven shaft, a frame for supporting rthe shafts, means providing a bearing support for one-endiof the driving shaft, and detachably supported -by -the laid of "the edge of an aperture in the frame, said aperture being -large lenough to permit withdrawal of the driving shaft and its associated `pulley structure through the aperture, saiddriv- -ing shaft-.havingf-a coupling extremity extending through :said bearing support providing means, and a bracket exterior of thefrarne, for a source of power, supported by said means.

9. -Inan adjustable ratio'transmission-mechanism, a driving shaft, an adjustable ,diameter pulley structure on the shaft, said structure having fa pair-of relatively axially adjustable pulley sections with opposed inclined vbelt engaging faces, `forming by relative axial-adjustment, var- -iable effective pulley diameters, a driven yshaft,

a frame for support the shafts,,meansprovidi-ng a bearingsupport for one end of the driving shaft, and detachablysupported by theaid ofzt-he edge of an Aaperture :in the frame, said .aperture being large enough to ,permit Withdrawal of the driving shaft .and its associated pulley `structure v throughthe aperture, said `Adriving shaft having a coupling vextremity Aextending vthrough said bearing support providing means, a bracket exterior of the frame, for a source of power, supported by said means, and bearing supporting means for the driven shaft, including standards by the aid of which the frame may be angularly adjusted about the axis of said driven shaft.

10. In an adjustable ratio transmission mechanism, a driving shaft, a driven shaft, pulley structures respectively on said shafts, one of said pulley structures having a pair of relatively axially adjustable pulley sections with opposed inclined belt engaging faces, forming by relative axial adjustment, variable effective pulley diameters, a frame for supporting the shafts, means providing a bearing support for one end of the driving shaft, and detachably supported by the frame, said means having provisions for supporting a source of power, said driving shaft extending through said means, and a wheel carried by said driving shaft at its extending end, and adapted to be driven by the source of power, said means being angularly adjustable about the axis of the driving shaft.

11. In an adjustable ratio transmission mechanism, a driving shaft, a driven shaft, pulley structures respectively on said shafts, one of said pulley structures having a pair of relatively axially adjustable pulley sections with opposed inclined belt engaging faces, forming by relative axial adjustment, variable effective pulley diameters, a frame for supporting the shafts, means providing a bearing support for one end of the driving shaft, and detachably supported by the frame, said means including a supporting foot member for a source of power, and adjustable about the axis of the driving shaft, said driving shaft extending through said means, and a wheel carried by said driving shaft at its extending end, and adapted to be driven by the source of power.

12. In an adjustable ratio transmission mechanism, a driving shaft, a driven shaft, pulley structures respectively on said shafts, one of said pulley structures having a pair of relatively axially adjustable pulley sections with opposed inclined belt engaging faces, forming by relative axial adjustment, variable effective pulley diameters, a frame for supporting the shafts, means providing a bearing support for one end of the driving shaft, and detachably supported by the frame, said means having provisions for supporting a source of power, said driving shaft extending through said means, a wheel carried by said driving shaft at its extending end, and adapted to be driven by the source of power, said means being angularly adjustable about the axis of the driving shaft, and bearing supporting means for the driven shaft, including standards by the aid of which the frame may be angularly adjusted about the axis of said driven shaft.

13. In an adjustable diameter pulley structure, a shaft, a pair of pulley sections mounted on the shaft, said pulley sections having opposed inclined faces, forming by relative axial adjustment, variable effective pulley diameters, one of said sections being axially adjustable on the shaft and having a hub, a spring mounted on and surrounding the shaft and exerting a resilient force on the hub to urge the said one of said sections in an axial direction, and means for radially supporting the shaft, including an axially movable member, a radial and thrust bearing structure interposed between said member and said hub, and serving to support the shaft, and a guide fo-r said axially movable member..

14. In an adjustable ratio transmission mechanism, a driving shaft, a driven shaft, cooperating pulley structures respectively on each shaft, belt means engaging the pulley structures, a frame for the mechanism, standards for supporting the frame, said standards being adjustably secured to the frame coaxially with one of said shafts, and means providing bearing supports for said one shaft detachably secured to said standards independently of the frame.

15. In a belt transmission mechanism, including a shaft with a pulley structure thereon and a frame, said frame having apertures disposed coaxially with respect to said shaft, said apertures being large enough to permit Withdrawal of the respective shaft and its pulley structure therethrough, a standard adjustably secured to the frame and supporting the frame by the aid of the edges of said apertures, said standards also having apertures large enough to permit passage of the said shafts and its pulley structure, and means providing bearing supports for said shaft and detachably supported by the aid of the edges of the apertures in said standards.

16. In a belt transmission mechanism, including a shaft with a pulley structure thereon, and a frame having apertures with alined cylindrical surfaces coaxial with said shafts, a standard having spaced cylindrical surfaces one of which is adapted to cooperate with the cylindrical surface on the frame for adjustably supporting the frame, means securing the standard to the frame in adjusted position, and means providing a bearing support for the shaft and detachably supported by means of a cylindrical surface which engages the other of said cylindrical surfaces on the standard.

17. A standard adapted to support a frame for a belt transmission mechanism with a shaft, and including a pair of spaced coaxial cylindrical surfaces, one of said surfaces being adapted to engage a cylindrical surface on the frame, the other of said surfaces being adapted to engage a cylindrical surface on a bearing support for said shaft, whereby the standard supports the frame as well as the bearing support, and means to secure the frame and the cover to the standard independently.

18. An adjustable ratio transmission including, a driving shaft and a driven shaft, one or more cooperating pulley structures respectively on each shaft, the pulley structures on at least one of the shafts having adjustable effective diameters, a frame, and belt means engaging the cooperating pulley structures, the combination therewith of means providing bearing supports for the shafts detachably secured on the sides of the frame, means forming a support for the frame, and a reduction gear mechanism including a frame detachably secured to one of said bearing support means to position said mechanism in operative relation to said driven shaft.

19. An adjustable ratio transmission including, a driving shaft and a driven shaft, one or more cooperating pulley structures respectively on each shaft, the pulley structures on at least one of the shafts having adjustable effective diameters, a frame, and belt means engaging the cooperating pulley structures, the combination therewith of means providing bearing supports for the shafts detachably secured on the sides of the frame, means supporting said frame for angular adjustment about the axis of one of said shafts, and a reduction gear mechanism including a frame detachably secured to one of said bearing support 

